Disc spring hydraulic mechanism energy storage cylinder and system

Abstract

The utility model discloses an energy storage cylinder and system of a disc spring hydraulic mechanism, and the energy storage cylinder comprises a cylinder body which is internally provided with a cavity, a piston, a sealing ring and a high-pressure oil channel; the piston is movably arranged in the cavity; the cavity comprises a working cavity and a low-pressure cavity; one end of the working cavity is connected with the high-pressure oil channel, the other end of the working cavity is connected with the low-pressure cavity, and the diameter of the low-pressure cavity is larger than that of the working cavity. The sealing ring is arranged on the periphery of the piston and used for preventing high-pressure oil entering from the high-pressure oil channel from flowing into the low-pressure cavity when the sealing ring is located in the working cavity. The high-pressure oil channel is used for inputting high-pressure oil to push the piston to move towards the low-pressure cavity or outputting the high-pressure oil to enable the piston to move towards the direction away from the low-pressure cavity. And the low-pressure cavity is used for collecting high-pressure oil flowing out of the sealing ring when the sealing ring is separated from the working cavity. The low-pressure oil cavity with the diameter larger than that of the working cavity is formed in the energy storage cylinder, high-pressure oil leakage occurs at the position of the sealing ring, and energy storage of the energy storage cylinder is stopped.

Description

Technical Field

[0001] The utility model relates to the technical field of switchgear, in particular to an energy storage cylinder of a disc spring hydraulic mechanism and a system. Background Art

[0002] Disc spring hydraulic mechanisms are widely used in switch applications. Their typical structural feature is the use of disc springs to store energy. The accumulator cylinder is an essential component of these mechanisms, consisting primarily of a cylinder body, piston, and cylinder head. Their operating principle is that an oil pump injects high-pressure oil into the rodless chamber of the accumulator cylinder through a pipeline, pushing the accumulator piston outward, compressing the disc springs and building up system pressure. Typically, disc spring hydraulic mechanisms monitor the compression of the disc springs to determine whether the preset pressure has been reached and then shut down the accumulator motor via a travel switch.

[0003] The accumulators currently used in disc spring hydraulic mechanisms have the following main problems: when the storage pressure reaches the design pressure and the storage control system fails to cut off the storage circuit due to a malfunction (such as a mechanical or electrical failure in the travel switch), the hydraulic system pressure continues to rise, which may cause damage to hydraulic system parts. For example, the storage piston may push open the cylinder cover, causing high-pressure oil leakage, or the combined disc spring may be over-compressed. These factors will cause structural damage and may cause personal injury. Utility Model Content

[0004] The utility model provides an energy storage cylinder and system of a disc spring hydraulic mechanism, which is used to solve the problem of how to prevent the energy storage cylinder from continuing to store energy when the energy storage control system fails due to a mechanical or electrical failure of a travel switch and cannot cut off the energy storage circuit, and to prevent the energy storage piston from continuing to move, causing the cylinder cover to be pushed open and causing high-pressure oil leakage or excessive compression of the combined disc spring.

[0005] The utility model provides a disc spring hydraulic mechanism energy storage cylinder, comprising: a cylinder body, wherein the cylinder body comprises a cavity, a piston, a sealing ring and a high-pressure oil channel;

[0006] The piston is movably arranged in the cavity;

[0007] The cavity includes a working chamber and a low-pressure chamber;

[0008] One end of the working chamber is connected to the high-pressure oil channel, and the other end of the working chamber is connected to the low-pressure chamber, and the diameter of the low-pressure chamber is larger than the diameter of the working chamber;

[0009] The sealing ring is arranged on the outer periphery of the piston and is used to isolate the high-pressure oil entering from the high-pressure oil channel from flowing into the low-pressure chamber when the sealing ring is in the working chamber;

[0010] The high-pressure oil channel is used to input high-pressure oil to push the piston toward the low-pressure chamber, or to output high-pressure oil to move the piston away from the low-pressure chamber;

[0011] The low-pressure chamber is used to collect high-pressure oil flowing out of the sealing ring when the sealing ring is separated from the working chamber.

[0012] Furthermore, the cavity also includes a transition cavity, which is arranged between the working cavity and the low-pressure cavity. The diameter of the transition cavity gradually increases, the smallest diameter end of the transition cavity is connected to the working cavity, and the largest diameter end of the transition cavity is connected to the low-pressure cavity.

[0013] Furthermore, the height of the transition cavity is greater than the height of the sealing ring.

[0014] Furthermore, the transition cavity is truncated cone-shaped.

[0015] Furthermore, the angle between the busbar of the transition cavity and the axis of the transition cavity is greater than zero and less than or equal to 30°.

[0016] Furthermore, the included angle between the busbar of the transition cavity and the axis of the transition cavity is greater than or equal to 15°.

[0017] Furthermore, the cylinder body further includes a low-pressure oil channel, which is connected to the low-pressure chamber and is used to output the high-pressure oil collected by the low-pressure chamber.

[0018] Furthermore, the diameter of the low-pressure cavity is greater than a preset value, which is the diameter of the cavity when the inlet speed of the high-pressure oil in the high-pressure oil channel is equal to the outlet speed of the high-pressure oil at the sealing ring.

[0019] The utility model provides an energy storage system of a disc spring hydraulic mechanism, comprising an energy storage cylinder, a connecting rod, a combined disc spring and a control assembly;

[0020] The piston of the energy storage cylinder is connected to the combined disc spring through the connecting rod, the middle part of the connecting rod passes through the bottom of the cylinder body, and the connecting rod is used to realize the movement of the piston to drive the combined disc spring disc to synchronously expand and contract;

[0021] The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch:

[0022] The oil pump is connected to the high-pressure oil channel, and the motor is connected to the oil pump, and the motor is used to drive the oil pump to rotate and suck in and generate high-pressure oil;

[0023] The first travel switch and the second travel switch are both connected to the combined disc spring;

[0024] The motor, the first travel switch and the second travel switch are arranged in a series circuit, and the first travel switch and the second travel switch are both normally closed switches;

[0025] The first travel switch is used to cut off the series circuit when the combined disc spring reaches a first compression amount, so that the motor stops running;

[0026] The second travel switch is used to cut off the series circuit and stop the motor when the combined disc spring reaches a second compression amount, and the second compression amount is less than the first compression amount.

[0027] Furthermore, the second travel switch is connected to an alarm device.

[0028] As can be seen from the above technical solution, the present invention has the following advantages: It provides a dual protection mechanism to prevent over-energy storage in disc spring hydraulic mechanisms. On the one hand, the present invention provides an energy storage system for a disc spring hydraulic mechanism. By adding a second travel switch to the series circuit, when the first travel switch fails, the second travel switch disconnects the series circuit, causing the motor to stop running, stopping energy storage in the energy storage cylinder and preventing the piston from moving further, thereby achieving the first level of protection. On the other hand, the utility model provides an energy storage cylinder of a disc spring hydraulic mechanism. When the first stroke switch and the second stroke switch both fail, a low-pressure oil chamber with a diameter larger than the working chamber is set in the energy storage cylinder. When the sealing ring moves from the working chamber into the low-pressure chamber as the piston moves, the gap between the piston and the inner wall of the low-pressure chamber is larger than the gap between the piston and the working chamber, so that the sealing ring cannot isolate the high-pressure oil, and high-pressure oil leakage occurs. That is, the high-pressure oil flows into the low-pressure chamber from the gap between the piston and the inner wall of the low-pressure chamber, and is further discharged through the low-pressure oil channel, resulting in a decrease in the pressure difference above and below the piston, so that the energy storage cylinder stops storing energy and the piston does not have enough power to continue moving, thereby avoiding the problem of the cylinder cover being pushed open and causing leakage of high-pressure oil or excessive compression of the combined disc spring, thereby achieving a second level of protection. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0030] Figure 1 This is a structural diagram of a disc spring hydraulic mechanism provided in an embodiment of the present utility model;

[0031] Figure 2This is a schematic diagram of the structure of a control component in an energy storage system of a disc spring hydraulic mechanism provided in an embodiment of the present utility model;

[0032] Figure 3 A schematic diagram of the relationship between a travel switch and the compression amount of a combined disc spring in an energy storage system of a disc spring hydraulic mechanism provided in an embodiment of the present utility model;

[0033] Figure 4 This is a schematic diagram of a state in which a sealing ring in a disc spring hydraulic mechanism provided in an embodiment of the present utility model is about to fall off a working chamber;

[0034] Figure numerals: 1. cylinder body; 2. piston; 3. sealing ring; 4. cylinder head; 5. combined disc spring; 6. high-pressure oil channel; 7. low-pressure oil channel; 8. connecting rod; 9. working chamber; 10. transition chamber; 11. low-pressure chamber; S1. first stroke switch; S2. second stroke switch; L1. first compression amount; L2. second compression amount; L3. third compression amount; d1. working chamber diameter; d2. low-pressure chamber diameter; θ, angle between the busbar of the transition chamber and the axis of the transition chamber. DETAILED DESCRIPTION

[0035] In order to make the purpose, features, and advantages of the present invention more obvious and easy to understand, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the embodiments described below are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0036] The terms "first," "second," "third," "fourth," and so forth (if any) in the specification and drawings of the present invention are used to distinguish similar objects and are not necessarily used to describe a particular order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate, so that the implementation of the present application described herein can, for example, be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or apparatus that includes a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to these processes, methods, products, or apparatuses.

[0037] See also Figure 1 , Figure 1 The embodiment of the utility model provides a disc spring hydraulic mechanism energy storage cylinder, comprising: a cylinder body 1, wherein the cylinder body 1 includes a cavity, a piston 2, a sealing ring 3, and a high-pressure oil channel 6;

[0038] The piston 2 is movably arranged in the cavity;

[0039] The cavity includes a working chamber 9 and a low-pressure chamber 11;

[0040] One end of the working chamber 9 is connected to the high-pressure oil channel 6, and the other end of the working chamber 9 is connected to the low-pressure chamber 11.

[0041] The diameter of the low-pressure chamber 11 is larger than the diameter of the working chamber 9;

[0042] The sealing ring 3 is provided at the middle of the outer periphery of the piston 2 and is used to isolate the high-pressure oil entering from the high-pressure oil channel 6 from flowing into the low-pressure chamber 11 when the sealing ring 3 is in the working chamber 9;

[0043] The high-pressure oil channel 6 is used to input high-pressure oil to push the piston 2 toward the direction close to the low-pressure chamber 11, or to output high-pressure oil to move the piston 2 away from the low-pressure chamber 11;

[0044] The low-pressure chamber 11 is used to collect high-pressure oil flowing out of the sealing ring 3 when the sealing ring is separated from the working chamber 9 .

[0045] like Figure 1 As shown, the diameter of the working chamber 9 is d1, the diameter of the low-pressure chamber 11 is d2, and d1<d2.

[0046] It is understandable that, in specific implementation, high-pressure oil is continuously input from the high-pressure oil channel 6 into the working chamber 9 located above the piston 2. The sealing ring 3 provided between the piston 2 and the working chamber 9 isolates the high-pressure oil from flowing into the bottom of the piston 2, thereby causing the high-pressure oil to push the piston 2 toward the low-pressure chamber 11. When the sealing ring 3 moves from the working chamber 9 into the low-pressure chamber 11 as the piston 2 moves, since the diameter of the working chamber 9 is greater than the diameter of the low-pressure chamber 11, the gap between the piston 2 and the inner wall of the low-pressure chamber 11 is greater than the gap between the piston 2 and the working chamber 9, making it impossible for the sealing ring 3 to isolate the high-pressure oil, resulting in internal leakage of high-pressure oil. That is, high-pressure oil flows into the low-pressure chamber 11 from the sealing ring 3, causing the pressure difference above and below the piston 2 to decrease, causing the energy storage cylinder to stop storing energy, and the piston 2 to have insufficient power to continue moving. Therefore, this embodiment can prevent the energy storage cylinder from continuing to store energy through internal leakage of high-pressure oil, so that the energy storage piston 2 does not have sufficient power to continue moving.

[0047] In a more specific embodiment, an annular groove is provided in the middle of the outer periphery of the piston 2 , and the sealing ring 3 is partially embedded in the annular groove.

[0048] In a more specific embodiment, a transition chamber 10 is further provided between the working chamber 9 and the low-pressure chamber 11. The diameter of the transition chamber 10 gradually increases. The smallest diameter end of the transition chamber 10 is connected to the working chamber 9, and the largest diameter end of the transition chamber 10 is connected to the low-pressure chamber 11.

[0049] It is understandable that, in specific implementation, the sealing ring 3 directly enters the large-diameter low-pressure chamber 11 from the small-diameter working chamber 9, and the sealing ring 3 instantly expands and rebounds. The large flow of high-pressure oil impacts the expanded and rebounded sealing ring 3. When the high-pressure oil impacts, stress concentration may occur at the contact points between the sealing ring 3 and the surrounding structure, and the edge parts may be subjected to higher pressure, making these parts more susceptible to damage. This embodiment sets a transition chamber 10 between the working chamber 9 and the low-pressure chamber 11. The diameter of the transition chamber 10 gradually increases, which can control the expansion and rebound speed of the sealing ring 3, and then control the outflow rate and outflow speed of the high-pressure oil from the sealing ring 3, reducing the impact of the high-pressure oil on the sealing ring 3, thereby avoiding damage to the sealing ring 3 and ensuring the recoverability of the sealing ring 3.

[0050] In a more specific embodiment, the inner wall of the transition chamber 10 is distributed with a plurality of steps with gradually increasing diameters, so that the sealing ring 3 expands and rebounds step by step.

[0051] In some more specific embodiments, the inner wall of the transition chamber 10 is a slope with a gradually increasing diameter, that is, the transition chamber is a truncated cone. It can be understood that in a specific implementation, the transition chamber 10 must meet the requirements of controlling the expansion and rebound speed of the sealing ring 3, and must also meet the requirements of being able to be compressed back into the working chamber 9 after the sealing ring 3 leaves the working chamber 9. In this embodiment, the inner wall of the transition chamber 10 is a slope, which can reduce the resistance of the inner wall of the transition chamber 10 during the process of the sealing ring 3 being compressed back into the working chamber 9.

[0052] In a more specific embodiment, the inclined surface is a smooth inclined surface.

[0053] In a more specific embodiment, the height of the transition chamber 10 is greater than the height of the sealing ring 3. It is understood that, in a specific implementation, if the height of the transition chamber 10 is less than the height of the sealing ring 3, the difference in expansion and rebound between the upper and lower portions of the sealing ring 3 is significant. Due to the uneven rebound of the sealing ring 3, stress concentration is likely to occur, leading to problems such as material fatigue and shape change, accelerating the aging of the sealing ring 3. Furthermore, the difference in rebound between the upper and lower portions of the sealing ring 3 due to the oil pressure acting on the upper portion of the sealing ring 3 further exacerbates the stress concentration phenomenon. This stress concentration may cause microscopic damage to the material inside the sealing ring 3, such as the formation of microcracks. In this embodiment, the height of the transition chamber 10 is greater than the height of the sealing ring 3, which helps to narrow the difference in expansion and rebound between the upper and lower portions of the sealing ring 3, ensuring that the contact pressure of the sealing ring 3 is evenly distributed as much as possible, and preventing damage to the structure of the sealing ring 3.

[0054] In a more specific embodiment, the angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is greater than zero and less than or equal to 30°. As shown in the figure, the angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is θ. It is understandable that, in specific implementation, too large an angle may lead to insufficient busbar length and axis length. When the sealing ring 3 is compressed from the transition chamber 10 back to the working chamber 9, it is easy to cause problems such as uneven compression and misalignment of the sealing ring 3. When the sealing ring 3 enters the inner hole between the working chamber 9 and the transition chamber 10, there is a risk of damage to the sealing ring cutting. The angle of this embodiment is less than 30°, which can ensure that the busbar and axis length of the transition chamber 10 are long enough. When the sealing ring 3 is compressed from the transition chamber 10 back to the working chamber 9, it is not easy to cause problems such as uneven compression and misalignment of the sealing ring 3, while avoiding the risk of damage to the sealing ring cutting.

[0055] In a more specific embodiment, the included angle between the generatrix of the transition chamber 10 and the axis of the transition chamber 10 is greater than or equal to 15°. It is understood that, in a specific implementation, if the included angle is too small, the generatrix and the axis of the transition chamber 10 will be too long, which will require an increase in the height of the cylinder body 1, which is not conducive to the compactness of the cylinder body 1 structure.

[0056] In a more specific embodiment, the angle between the busbar of the transition chamber 10 and the axis of the transition chamber 10 is θ, 15°≤θ≤30°, so that the inner wall of the transition chamber 10 can effectively guide the sealing ring 3 to separate from the working chamber 9, while preventing the sealing ring 3 from expanding too quickly and being damaged by the impact of high-pressure oil.

[0057] In a more specific embodiment, a cylinder cover 4 is provided at the bottom of the transition chamber 10 .

[0058] In a more specific embodiment, the cylinder body 1 further includes a low-pressure oil passage 7 connected to the low-pressure chamber 11. The low-pressure oil passage 7 is used to output the high-pressure oil collected by the low-pressure chamber 11. It will be appreciated that, in a specific implementation, the space within the cylinder body 1 is limited. To ensure that the low-pressure chamber 11 can fully collect the high-pressure oil leaking from the sealing ring 3 before the accumulator cylinder stops storing energy, the low-pressure oil passage 7 is provided in this embodiment.

[0059] In a more specific embodiment, the low-pressure oil channel is provided on one side of the low-pressure chamber 11 .

[0060] In a more specific embodiment, the distance between the sealing ring 3 and the bottom of the piston 2 is smaller than the height of the low-pressure chamber 11 .

[0061] In a more specific embodiment, the diameter of the low-pressure chamber 11 is greater than a preset value, which is the diameter of the chamber when the high-pressure oil entering the high-pressure oil channel 6 is equal to the high-pressure oil flowing out of the sealing ring 3.

[0062] It should be noted that when the speed at which high-pressure oil enters the high-pressure oil channel 6 is equal to the speed at which high-pressure oil flows out of the sealing ring 3, the energy storage cylinder stops storing energy, the piston 2 stops moving toward the low-pressure chamber 11, and the combined disc spring 5 stops compressing.

[0063] It can be understood that, in a specific implementation, when the diameter of the low-pressure chamber 11 is equal to the preset value, the gap between the low-pressure chamber 11 and the piston 2 just satisfies the requirement that the oil outflow rate from the sealing ring 3 is equal to the high-pressure oil inflow rate from the high-pressure oil passage 6. This embodiment has the following advantages: the diameter of the low-pressure chamber 11 is larger than the preset value.

[0064] On the one hand, the low-pressure chamber 11 is larger than the preset value. Even if the sealing ring 3 enters the low-pressure chamber 11, it can at least ensure that the sealing ring 3 cannot seal and the high-pressure oil leaks out. This solves the problem of how to prevent the energy storage cylinder from continuing to store energy when the energy storage control system fails due to a mechanical or electrical failure of the travel switch and cannot cut off the energy storage circuit. It also prevents the energy storage piston 2 from continuing to move, causing the cylinder cover 4 to be pushed open, causing high-pressure oil leakage or excessive compression of the combined disc spring 5.

[0065] On the other hand, when the low-pressure chamber 11 is greater than the preset value, that is, the diameter of the transition chamber 10 can reach the preset value, it can ensure that the sealing ring 3 stops storing energy in the transition chamber 10, the piston 2 stops moving toward the low-pressure chamber 11, and the combined disc spring 5 stops compressing. The sealing ring 3 returns from the transition chamber 10 to the working chamber 9. Compared with the sealing ring 3 returning from the low-pressure chamber 11 to the working chamber 9, the return deformation of the sealing ring 3 changes less, which is beneficial to protecting the sealing ring 3.

[0066] On the other hand, since the low-pressure oil passage 7 is disposed on one side of the low-pressure chamber 11, the flow direction of the high-pressure oil in the low-pressure chamber 11 changes. When the sealing ring 3 falls into the low-pressure chamber 11, it is easy to cause uneven force on the sealing ring 3, which can easily cause the sealing ring 3 to be misaligned and damaged. This embodiment ensures that the sealing ring 3 stops storing energy when it is in the transition chamber 10, thus avoiding the recurrence of this problem.

[0067] In a more specific embodiment, the difference between the diameter of the low-pressure chamber 11 and the diameter of the working chamber 9 is greater than 2 mm.

[0068] Therefore, the disc spring hydraulic mechanism energy storage cylinder provided in this embodiment has a smooth sealing structure failure and recovery function, which can ensure that the internal structure of the hydraulic system is not damaged after a failure occurs, improve the safety of the debugging and operation process, and reduce maintenance costs.

[0069] This embodiment provides an energy storage system of a disc spring hydraulic mechanism, comprising the energy storage cylinder, the combined disc spring 5 and the control assembly in the above embodiment;

[0070] The piston 2 in the energy storage cylinder is connected to the combined disc spring 5 via the connecting rod 8. The middle portion of the connecting rod 8 passes through the bottom of the low-pressure chamber 11. The connecting rod 8 is used to synchronize the movement of the piston 2 and the expansion and contraction of the combined disc spring 5.

[0071] The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch:

[0072] The oil pump is connected to the high-pressure oil channel 6, and the motor is connected to the oil pump, and the motor is used to drive the oil pump to rotate and suck in and generate high-pressure oil;

[0073] The first travel switch S1 and the second travel switch S2 are both connected to the combined disc spring 5;

[0074] The motor, the first travel switch S1 and the second travel switch S2 are arranged in a series circuit, and the first travel switch S1 and the second travel switch S2 are both normally closed switches;

[0075] The first travel switch S1 is used to cut off the series circuit when the combined disc spring 5 reaches the first compression amount L1, so that the motor stops running;

[0076] The second travel switch S2 is used to cut off the series circuit and stop the motor when the combined disc spring 5 reaches a second compression amount L2, and the second compression amount L2 is less than the first compression amount L1.

[0077] In a more specific embodiment, the second travel switch S2 is connected to an alarm device. When the combined disc spring 5 reaches the second compression amount L2, the second travel switch S2 is triggered and the alarm device is also triggered, notifying personnel to promptly handle the fault. Even when the second travel switch S2 fails, the alarm device can still be triggered.

[0078] It can be understood that the existing disc spring hydraulic mechanism energy storage control system is mainly composed of a motor oil pump system, a first travel switch S1, other secondary control elements and a power supply, wherein the first travel switch S1 is a normally closed micro switch and is connected in series to the control circuit of the energy storage motor. When the combined disc spring 5 is compressed to the first compression amount L1, the first travel switch S1 is disconnected, and the energy storage motor is controlled to stop rotating.

[0079] In this embodiment, in terms of the method for preventing over-energy storage, a second travel switch S2 for high oil pressure warning is added. When the first travel switch S1 fails, the combined disc spring 5 is compressed to the first compression amount L1 and then further compressed to the second compression amount L2. The second travel switch S2 will cut off the motor circuit and sound an alarm. If the energy storage cylinder of the disc spring hydraulic mechanism has not stopped storing energy at this time, it will rely on the energy storage cylinder structure for protection.

[0080] like Figure 3 As shown, when the combined disc spring 5 is compressed to the third compression amount L3 and is still storing energy, the energy storage piston 2 continues to move downward, and the sealing ring 3 will enter the inclined surface and then expand outward, the sealing effect will weaken, and the sealing effect will accelerate as the energy storage piston 2 continues to move downward. In this process, internal leakage will occur, and at a certain moment, it will reach a balance with the pressure replenishment process, that is, when the high-pressure oil entering the high-pressure oil channel 6 is equal to the outflow speed at the sealing ring 3, the energy storage piston 22 will be prevented from continuing to move downward. The expansion speed of the sealing ring 3 in this embodiment is controllable, which can protect the sealing ring 3 from being damaged by excessive flow of hydraulic oil, and it is recoverable. After a fault occurs, there is no need to disassemble and repair the energy storage cylinder and the hydraulic system.

[0081] Compared to existing technologies, the energy storage system of a disc spring hydraulic mechanism in this embodiment provides dual protection. First, it provides a second travel switch S2 for high oil pressure warning, helping maintenance personnel to detect faults in a timely manner. Second, the energy storage cylinder structure ensures that over-energy storage will not cause safety accidents. The recoverability of the seal ring 3 in this structure removes the hydraulic system from the repair and recovery of faults, greatly improving maintenance efficiency. This embodiment maximizes the energy storage safety of the disc spring hydraulic mechanism and reduces the safety risks caused by mechanical or electrical failures of the first travel switch S1.

[0082] Based on the above energy storage system, this embodiment provides a control method, including:

[0083] The first level of protection is achieved by:

[0084] When the combined disc spring 5 reaches the first compression amount L1, the first travel switch S1 is disconnected, cutting off the series circuit, stopping the motor from running, stopping the high-pressure oil from entering the high-pressure oil channel 6, and realizing that the piston 2 stops moving and the combined disc spring 5 stops compressing;

[0085] When the combined disc spring 5 reaches the second compression amount L2, the series circuit is cut off, the motor stops running, and the high-pressure oil is stopped from being input from the high-pressure oil channel 6, so that the piston 2 stops moving and the combined disc spring 5 stops compressing.

[0086] In a more specific embodiment, a method for implementing the second level of protection is provided as follows:

[0087] When the combined disc spring 5 reaches the third compression amount L3, the sealing ring 3 on the piston 2 separates from the working chamber 9 and enters the transition chamber 10, the gap between the piston 2 and the transition chamber 10 gradually increases, the sealing ring 3 gradually rebounds, and the high-pressure oil passes through the transition chamber 10 into the low-pressure chamber 11 and flows out from the low-pressure oil channel 7. The third compression amount L3 is greater than the second compression amount L2.

[0088] When the inflow speed of the high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed at the sealing ring 3, the piston 2 stops moving toward the low-pressure chamber 11 and the combined disc spring 5 stops compressing.

[0089] It should be noted that, in actual application, when the entry speed of high-pressure oil from the high-pressure oil channel 6 is equal to the outflow speed from the sealing ring 3, the force exerted by the high-pressure oil on the piston 2 is equal to the force exerted by the elastic potential energy of the combined disc spring 5 on the piston 2. When the force on the piston 2 is balanced, the piston 2 stops moving toward the low-pressure chamber 11 and the combined disc spring 5 stops compressing.

[0090] It is understandable that this embodiment provides a dual protection control method for preventing disc spring hydraulic mechanism from over-storage of energy, which increases the protection and early warning risk of disc spring hydraulic mechanism over-storage of energy and increases the safety of the system.

[0091] In a more specific embodiment, a method for achieving a recovery seal is provided as follows:

[0092] When the sealing ring 3 is separated from the working chamber 9 and is in the transition chamber 10, after the piston 2 stops moving, the motor is manually stopped, and part of the high-pressure oil is released from the high-pressure oil channel 6 to reduce the oil pressure in the chamber. The elastic potential energy of the combined disc spring 5 is greater than the oil pressure in the chamber, so that the piston 2 moves away from the low-pressure chamber 11, and the sealing ring 3 enters the working chamber 9 from the transition chamber 10 to resume the sealing function.

[0093] It can be understood that this embodiment sets a transition chamber 10 between the working chamber 9 and the low-pressure chamber 11, and makes specific restrictions on the height of the transition chamber 10, the angle of the bevel, and the diameter of the low-pressure chamber 11. On this basis, the structural integrity and recoverability of the sealing ring 3 can be ensured. Therefore, the sealing ring 3 of this embodiment can return to the working chamber 9 as the piston 2 resumes its sealing function.

[0094] The above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments can still be modified, or some of the technical features thereof can be replaced by equivalents. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. A disc spring hydraulic mechanism accumulator cylinder, characterized in that: include: A cylinder body (1), wherein the cylinder body (1) includes a cavity, a piston (2), a sealing ring (3) and a high-pressure oil channel (6); The piston (2) is movably arranged in the cavity; The cavity comprises a working chamber (9) and a low-pressure chamber (11); One end of the working chamber (9) is connected to the high-pressure oil channel (6), and the other end of the working chamber (9) is connected to the low-pressure chamber (11), and the diameter of the low-pressure chamber (11) is larger than the diameter of the working chamber (9); The sealing ring (3) is arranged on the outer periphery of the piston (2) and is used to isolate the high-pressure oil entering from the high-pressure oil channel (6) from flowing into the low-pressure chamber (11) when the sealing ring (3) is in the working chamber (9); The high-pressure oil channel (6) is used to input high-pressure oil to push the piston (2) toward the low-pressure chamber (11), or to output high-pressure oil to move the piston (2) toward the low-pressure chamber (11); The low-pressure chamber (11) is used to collect high-pressure oil flowing out of the sealing ring (3) when the sealing ring (3) is separated from the working chamber (9).

2. The disc spring hydraulic mechanism accumulator cylinder according to claim 1, characterized in that: The cavity further comprises a transition cavity (10), wherein the transition cavity (10) is arranged between the working cavity (9) and the low-pressure cavity (11), and the diameter of the transition cavity (10) gradually increases, wherein the smallest diameter end of the transition cavity (10) is connected to the working cavity (9), and the largest diameter end of the transition cavity (10) is connected to the low-pressure cavity (11).

3. The disc spring hydraulic mechanism accumulator cylinder according to claim 2, characterized in that: The height of the transition chamber (10) is greater than the height of the sealing ring (3).

4. The disc spring hydraulic mechanism accumulator cylinder according to claim 2, characterized in that: The transition chamber (10) is in the shape of a truncated cone.

5. The disc spring hydraulic mechanism accumulator cylinder according to claim 4, characterized in that: The included angle between the busbar of the transition cavity (10) and the axis of the transition cavity (10) is greater than zero and less than or equal to 30°.

6. The disc spring hydraulic mechanism accumulator cylinder according to claim 5, characterized in that: The included angle between the busbar of the transition cavity (10) and the axis of the transition cavity (10) is greater than or equal to 15°.

7. The disc spring hydraulic mechanism accumulator cylinder according to claim 1, characterized in that: The cylinder body (1) further comprises a low-pressure oil channel (7), the low-pressure oil channel (7) being connected to the low-pressure chamber (11), and the low-pressure oil channel (7) being used to output the high-pressure oil collected by the low-pressure chamber (11).

8. The disc spring hydraulic mechanism accumulator cylinder according to claim 1, 2 or 7, characterized in that: The diameter of the low-pressure cavity (11) is greater than a preset value, which is the diameter of the cavity when the inlet speed of the high-pressure oil in the high-pressure oil channel (6) is equal to the outlet speed of the high-pressure oil at the sealing ring (3).

9. An energy storage system for a disc spring hydraulic mechanism, characterized in that: It comprises the energy storage cylinder, connecting rod (8), combined disc spring (5) and control assembly according to any one of claims 1 to 8; The piston (2) of the energy storage cylinder is connected to the combined disc spring (5) via the connecting rod (8), the middle portion of the connecting rod (8) passes through the bottom of the cylinder body (1), and the connecting rod (8) is used to realize the movement of the piston (2) and drive the combined disc spring (5) to synchronously expand and contract; The control assembly includes a motor, an oil pump, a first travel switch and a second travel switch: The oil pump is connected to the high-pressure oil channel (6), and the motor is connected to the oil pump, and the motor is used to drive the oil pump to rotate and suck in and generate high-pressure oil; The first travel switch and the second travel switch are both connected to the combined disc spring (5); The motor, the first travel switch and the second travel switch are arranged in a series circuit, and the first travel switch and the second travel switch are both normally closed switches; The first travel switch is used to cut off the series circuit when the combined disc spring (5) reaches a first compression amount, so as to stop the motor; The second travel switch is used to cut off the series circuit and stop the motor when the combined disc spring (5) reaches a second compression amount, and the second compression amount is less than the first compression amount.

10. The energy storage system of the disc spring hydraulic mechanism according to claim 9, characterized in that: The second travel switch is connected to an alarm device.

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